WO1989003477A1 - Positive displacement fluid machines - Google Patents
Positive displacement fluid machines Download PDFInfo
- Publication number
- WO1989003477A1 WO1989003477A1 PCT/GB1988/000839 GB8800839W WO8903477A1 WO 1989003477 A1 WO1989003477 A1 WO 1989003477A1 GB 8800839 W GB8800839 W GB 8800839W WO 8903477 A1 WO8903477 A1 WO 8903477A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- housing
- reciprocatory
- transverse
- reciprocatory member
- machine according
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
- F01B9/00—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups
- F01B9/02—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft
- F01B9/023—Reciprocating-piston machines or engines characterised by connections between pistons and main shafts and not specific to preceding groups with crankshaft of Bourke-type or Scotch yoke
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B1/00—Methods of steam generation characterised by form of heating method
- F22B1/28—Methods of steam generation characterised by form of heating method in boilers heated electrically
Definitions
- the present invention relates to positive displacement fluid machines such as pumps and motors and is particularly suitable for such machines which are subject to changes in temperature for example between the operating and non-operating conditions.
- the invention is thus especially applicable to internal combustion engines.
- a positive displacement fluid machine comprising a housing, a reciprocatory member mounted for reciprocation in the housing to vary the volume of a fluid chamber, a shaft mounted for rotation in the housing, and drive means for converting rotary motion of the shaft into reciprocatory motion of the reciprocatory member and/or vice-versa, wherein the reciprocatory member carries a pair of ⁇ paced-apart lateral guide members on opposite sides of the reciprocatory member cooperating with respective guides carried by the housing and the lateral guide members are interconnected by means having substantially the same linear thermal expansion as the portion of the housing extending between the two guides.
- the reciprocatory member will, for reasons of strength, be made of a material which is quite different from that of the housing.
- the latter may for example be of aluminium alloy whereas the reciprocatory member may be of steel.
- the two guide members are interconnected by a transverse element carried by the reciprocatory member, the transverse element having a thermal expansion substantially equal to that of the housing portion interconnecting the two guides.
- At least part of the transverse member is directly exposed to ambient conditions within the housing, for example by means of cut-out portions of the reciprocatory member leaving the surface of the transverse member exposed.
- the drive means may comprise a parallel-sided drive block engaged in a transverse guideway in the reciprocatory member and rotatably mounted on an eccentric portion of the drive shaft.
- the guide members are preferably at or near the other end, on the opposite side of the transverse guideway to the piston.
- Figure 1 is a vertical cross section through a three-cylinder radial internal combustion engine, the cylinder heads and other conventional parts of which have been ommitted for clarity;
- Figure 2 shows a modification to a portion of Figure 1 on an enlarged scale
- Figure 3 is a view on the line III-III of Figure 2.
- the internal combustion engine shown in Figure 1 comprises three cylinders A,B, and C.
- the cylinders A and C are horizontally opposed while the cylinder B has its axis vertical.
- the axes of the three cylinders all intersect the axis 1 of a single-throw crank shaft which is mounted in bearings (not shown) in a housing or crank case 2 formed mainly by two aluminium alloy castings secured together by suitable tie bolts (not shown) at a joint face which coincides with the plane of the drawing.
- Each cylinder has a cylinder liner 3 which is clamped between the two crank case halves.
- Respective pistons 4 A,B and C are slidable in the cylinders and each have a pair of compression rings 5 and an oil-control piston ring assembly 6.
- Water passages are formed in the crank case halves around each of the cylinders and the corresponding passages in the two crank case halves interconnect by openings 7 which are surrounded by annular seatings 8 to accomodate O-rlngs (not shown).
- the various drilled passages for the tie bolts to clamp the crank case halves together are shown at H.
- each cylinder is in the completed engine closed by a cylinder head (not shown) which may be of any required construction typically for four stroke operation and formed with one or more inlet and one or more exhaust valves together with fuel injection apparatus (especially for a compression ignition engine) and a spark plug in the case of a spark-ignition engine.
- a cylinder head (not shown) which may be of any required construction typically for four stroke operation and formed with one or more inlet and one or more exhaust valves together with fuel injection apparatus (especially for a compression ignition engine) and a spark plug in the case of a spark-ignition engine.
- the piston 4B forms part of a vertically reciprocating assembly 11.
- the piston 4B is secured by a gudgeon pin 12B to the stem of a T-shaped connecting rod 13B the opposite face 14B of which is flat, hardened and highly polished to form a transverse guide surface cooperating with a drive block 15 which is rotatably mounted on a crank pin portion 16 of the crank shaft, the crank pin axis being shown at 17.
- a second transverse guide surface 18B is formed on a bottom cap member 18 which is secured to the link member 13B by tie rods 19 located within spacer tubes 20.
- the ends of the tie rods are screw threaded. At their lower ends they are engaged in screw threaded holes 21 in the bottom cap 18 while at their upper ends they carry nuts 22.
- the drive block 15 is divided diagonally into two parts of triangular cross-section secured together by dowel screws 23 and its upper and lower faces are recessed to accomodate plates 24 of appropriate bearing material, each plate 24 having a central hole 25 through which lubricant can be supplied from the crank shaft through passages 26.
- the components 13B, 18,19 and 20 need to be of a higher strength material than that required for the crank case 2 and are accordingly of steel, the guideway surfaces being suitably hardened.
- hardened steel guide plates 31 are mounted in recesses in the crank case walls and each may be formed with a securing lug 32 through which passes a securing screw 33 into a tapped hole in one of the crank case halves.
- the bottom cap 18 carries guide pads 34 to cooperate with the guide plates 31, being slidably guided thereby.
- the guide pads are not directly secured to the bottom cap but are instead fixed to the ends of a cylindrical bar 35 of aluminium alloy housed in a longitudinal bore 36 extending throughout the length of the end cap 18.
- the pads 34 may be of an appropriate bearing material or steel coated with a low friction coating. Each pad is secured to its respective end of the bar 35 by a pair of counter sunk screws 37 the heads of which lie below the surface of the pad 34.
- a locating dowel pin 38 extends through aligned bores in the bottom cap and the bar and has an enlarged screw threaded end 39 by means of which it is secured in the bottom cap 18.
- Parts of the bottom cap 18 are cut away or recessed at 40 to expose the surface of the bar 35 to the oil mist within the crank case. This ensures that the bar 35 and crank case are always at substantially the same temperature. By arranging that the bar 35 has substantially the same coefficient of thermal expansion as the material of the crank case, any required bearing clearances between the pad 34 on the side which is temporarily unloaded and its guide plate 31 will be constant for all operating temperatures.
- a second reciprocatory assembly 41 comprises the other two pistons 4A and 4C each of which is secured to a respective connecting link 13A, 13C which are bolted together by a pair of tie bolts 42 with spacers 43 between the two connecting links to define a transverse guideway similar that of the first assembly.
- Slidable in this guideway is a second drive block which may, if required, be formed by an extension of the drive block 15.
- the total mass of the first reciprocatory assembly 11 is made equal to that of the second reciprocatory assembly 41. Since both assemblies are controlled by the same crank pin 16, and have their axes at right angles with each other they reciprocate in quadrature and have the same effect on the crank shaft as a single mass equal to that of either reciprocatory assembly concentrated on the axis 17 of the crank pin. This eccentric mass acting on the crank shaft can then be balanced by balance weights 49 on the crank shaft webs on the opposite side of the crank shaft axis 25 to the crank pin 16.
- crank shaft In the position shown in the drawing, the crank shaft is at its bottom dead centre position. Even so, the bottom cap 18 is clear of a sump 52 formed in the lower part of the crank case. Oil churning losses are thus avoided.
- the centre of gravity of the reciprocatory assembly 11 will not coincide with a horizontal plane through the crank pin axis 17 but will be above this plane. This will not however not cause any unbalance forces which would cause vibration.
- each guide 32' is accurately located by means of a dowel pin 51 and secured to the crankcase half by a pair of cap-screws 52.
- the 35' is anchored at its mid-point by means of a transverse pin 53 the ends of which are peened over at 54.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Sustainable Energy (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
In a positive displacement fluid machine such as an internal combustion engine, a reciprocatory assembly (11) carrying a piston (4B) is slidably guided at its end opposite the piston by means of a pair of widely spaced guide pads (34) sliding on guide plates (31) secured to the housing (2) of the machine. The guide pads (34) are secured to opposite ends of a rod (35) having a coefficient of linear thermal expansion similar to that of the housing (2) so that the guide clearances remain constant over a wide range of operating temperatures.
Description
_ λ _
POSITIVE DISPLACEMENT FLUID MACHINES
The present invention relates to positive displacement fluid machines such as pumps and motors and is particularly suitable for such machines which are subject to changes in temperature for example between the operating and non-operating conditions. The invention is thus especially applicable to internal combustion engines.
According to the present invention there is provided a positive displacement fluid machine comprising a housing, a reciprocatory member mounted for reciprocation in the housing to vary the volume of a fluid chamber, a shaft mounted for rotation in the housing, and drive means for converting rotary motion of the shaft into reciprocatory motion of the reciprocatory member and/or vice-versa, wherein the reciprocatory member carries a pair of εpaced-apart lateral guide members on opposite sides of the reciprocatory member cooperating with respective guides carried by the housing and the lateral guide members are interconnected by means having substantially the same linear thermal expansion as the portion of the housing extending between the two guides.
Typically the reciprocatory member will, for reasons of strength, be made of a material which is quite different from that of the housing. The latter may for example be of aluminium alloy whereas the reciprocatory member may be of steel. Advantageously, the two guide members are interconnected by a transverse element carried by the reciprocatory member, the transverse element having a thermal expansion substantially equal to that of the housing portion interconnecting the two guides.
With such an arrangement in accordance with the invention, optimum bearing clearances can be established and maintained between the guide members and their guides regardless of variations in temperature.
Advantageously, at least part of the transverse member is
directly exposed to ambient conditions within the housing, for example by means of cut-out portions of the reciprocatory member leaving the surface of the transverse member exposed.
The drive means may comprise a parallel-sided drive block engaged in a transverse guideway in the reciprocatory member and rotatably mounted on an eccentric portion of the drive shaft. Where the reciprocatory member carries a piston at one end, the guide members are preferably at or near the other end, on the opposite side of the transverse guideway to the piston.
The invention will now be further described by way of example with reference to the accompanying drawing in which:
Figure 1 is a vertical cross section through a three-cylinder radial internal combustion engine, the cylinder heads and other conventional parts of which have been ommitted for clarity;
Figure 2 shows a modification to a portion of Figure 1 on an enlarged scale; and
Figure 3 is a view on the line III-III of Figure 2.
The internal combustion engine shown in Figure 1 comprises three cylinders A,B, and C. The cylinders A and C are horizontally opposed while the cylinder B has its axis vertical. The axes of the three cylinders all intersect the axis 1 of a single-throw crank shaft which is mounted in bearings (not shown) in a housing or crank case 2 formed mainly by two aluminium alloy castings secured together by suitable tie bolts (not shown) at a joint face which coincides with the plane of the drawing. Each cylinder has a cylinder liner 3 which is clamped between the two crank case halves. Respective pistons 4 A,B and C are slidable in the cylinders and each have a pair of compression rings 5 and an oil-control piston ring assembly 6.
Water passages are formed in the crank case halves around each of the cylinders and the corresponding passages in the two crank case halves interconnect by openings 7 which are surrounded by annular seatings 8 to accomodate O-rlngs (not shown). The various drilled passages for the tie bolts to clamp the crank case halves together are shown at H.
The radially outer end of each cylinder is in the completed engine closed by a cylinder head (not shown) which may be of any required construction typically for four stroke operation and formed
with one or more inlet and one or more exhaust valves together with fuel injection apparatus (especially for a compression ignition engine) and a spark plug in the case of a spark-ignition engine.
The piston 4B forms part of a vertically reciprocating assembly 11. The piston 4B is secured by a gudgeon pin 12B to the stem of a T-shaped connecting rod 13B the opposite face 14B of which is flat, hardened and highly polished to form a transverse guide surface cooperating with a drive block 15 which is rotatably mounted on a crank pin portion 16 of the crank shaft, the crank pin axis being shown at 17.
A second transverse guide surface 18B is formed on a bottom cap member 18 which is secured to the link member 13B by tie rods 19 located within spacer tubes 20. The ends of the tie rods are screw threaded. At their lower ends they are engaged in screw threaded holes 21 in the bottom cap 18 while at their upper ends they carry nuts 22.
The drive block 15 is divided diagonally into two parts of triangular cross-section secured together by dowel screws 23 and its upper and lower faces are recessed to accomodate plates 24 of appropriate bearing material, each plate 24 having a central hole 25 through which lubricant can be supplied from the crank shaft through passages 26.
In view of the high accelerations to which the reciprocatory assembly 11 is subjected in operation, the components 13B, 18,19 and 20 need to be of a higher strength material than that required for the crank case 2 and are accordingly of steel, the guideway surfaces being suitably hardened.
While the upper end of the reciprocatory assembly 11 is laterally guided by the piston 4B in its cylinder, provision must be made to guide the lower end of the assembly particularly in view of the moment exerted by the crank pin and drive block on the assembly about the axis of the pin 12b in all positions in which the crank pin and drive block are not on the centre line of the cylinder B.
Accordingly, hardened steel guide plates 31 are mounted in recesses in the crank case walls and each may be formed with a securing lug 32 through which passes a securing screw 33 into a tapped hole in one of the crank case halves. The bottom cap 18
carries guide pads 34 to cooperate with the guide plates 31, being slidably guided thereby. In view of the length of the bottom cap 18 and consequent variations in the distance between the guide pads caused by variations in temperature, the guide pads are not directly secured to the bottom cap but are instead fixed to the ends of a cylindrical bar 35 of aluminium alloy housed in a longitudinal bore 36 extending throughout the length of the end cap 18. The pads 34 may be of an appropriate bearing material or steel coated with a low friction coating. Each pad is secured to its respective end of the bar 35 by a pair of counter sunk screws 37 the heads of which lie below the surface of the pad 34.
To ensure the correct position and orientation of the bar 35, a locating dowel pin 38 extends through aligned bores in the bottom cap and the bar and has an enlarged screw threaded end 39 by means of which it is secured in the bottom cap 18.
Parts of the bottom cap 18 are cut away or recessed at 40 to expose the surface of the bar 35 to the oil mist within the crank case. This ensures that the bar 35 and crank case are always at substantially the same temperature. By arranging that the bar 35 has substantially the same coefficient of thermal expansion as the material of the crank case, any required bearing clearances between the pad 34 on the side which is temporarily unloaded and its guide plate 31 will be constant for all operating temperatures.
A second reciprocatory assembly 41 comprises the other two pistons 4A and 4C each of which is secured to a respective connecting link 13A, 13C which are bolted together by a pair of tie bolts 42 with spacers 43 between the two connecting links to define a transverse guideway similar that of the first assembly. Slidable in this guideway is a second drive block which may, if required, be formed by an extension of the drive block 15.
The total mass of the first reciprocatory assembly 11 is made equal to that of the second reciprocatory assembly 41. Since both assemblies are controlled by the same crank pin 16, and have their axes at right angles with each other they reciprocate in quadrature and have the same effect on the crank shaft as a single mass equal to that of either reciprocatory assembly concentrated on the axis 17 of the crank pin. This eccentric mass acting on the crank shaft can
then be balanced by balance weights 49 on the crank shaft webs on the opposite side of the crank shaft axis 25 to the crank pin 16.
In the position shown in the drawing, the crank shaft is at its bottom dead centre position. Even so, the bottom cap 18 is clear of a sump 52 formed in the lower part of the crank case. Oil churning losses are thus avoided. The centre of gravity of the reciprocatory assembly 11 will not coincide with a horizontal plane through the crank pin axis 17 but will be above this plane. This will not however not cause any unbalance forces which would cause vibration.
In the modified construction shown in Figures 2 and 3, each guide 32' is accurately located by means of a dowel pin 51 and secured to the crankcase half by a pair of cap-screws 52. The 35' is anchored at its mid-point by means of a transverse pin 53 the ends of which are peened over at 54.
Claims
1. A positive displacement fluid machine comprising a housing, a reciprocatory member mounted for reciprocation in the housing to vary the volume of a fluid chamber, a shaft mounted for rotation in the housing, and drive means for converting rotary motion of the shaft into reciprocatory motion of the reciprocatory member and/or vice-versa, wherein the reciprocatory member carries a pair of spaced-apart lateral guide members on opposite sides of the reciprocatory member cooperating with respective guides carried by the housing and the lateral guide members are interconnected by means having substantially the same linear thermal expansion as the portion of the housing extending between the two guides.
2. A machine according to claim 1, wherein the housing is made of aluminium alloy and the reciprocatory member is of steel.
3. A machine according to claim 1, wherein the two guide members are interconnected by a transverse element carried by the reciprocatory member, the transverse element having a thermal expansion substantially equal to that of the housing portion interconnecting the two guides.
4. A machine according to claim 3, wherein at least part of the transverse member is directly exposed to ambient conditions within the housing.
5. A machine according to claim 4, wherein the transverse member extends through cut-out portions of the reciprocatory member, leaving the surface of the transverse member exposed.
6. A machine according to claim 1, wherein the drive means comprises a parallel-sided drive block engaged in a transverse guideway in the reciprocatory member and rotatably mounted on an eccentric portion of the drive shaft, the reciprocatory member carrying a piston at one end, the guide members being at or near the other end, on the opposite side of the transverse guideway to the _ _
piston.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1019890701042A KR890701876A (en) | 1987-10-09 | 1988-10-10 | Displaceable Fluid Engine |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB878723712A GB8723712D0 (en) | 1987-10-09 | 1987-10-09 | Positive displacement fluid machines |
| GB8723712 | 1987-10-09 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO1989003477A1 true WO1989003477A1 (en) | 1989-04-20 |
Family
ID=10625034
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/GB1988/000839 WO1989003477A1 (en) | 1987-10-09 | 1988-10-10 | Positive displacement fluid machines |
Country Status (4)
| Country | Link |
|---|---|
| KR (1) | KR890701876A (en) |
| AU (1) | AU2545788A (en) |
| GB (1) | GB8723712D0 (en) |
| WO (1) | WO1989003477A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990014501A1 (en) * | 1989-05-22 | 1990-11-29 | Collins Motor Corporation Limited | Multi-cylinder positive displacement machines |
| CN112746896A (en) * | 2019-10-29 | 2021-05-04 | 赛德动力科技(广东)有限公司 | Internal combustion engine with improved oil pump device |
| CN112746897A (en) * | 2019-10-29 | 2021-05-04 | 赛德动力科技(广东)有限公司 | Internal combustion engine with targeted engine lubrication |
| CN112746900A (en) * | 2019-10-29 | 2021-05-04 | 赛德动力科技(广东)有限公司 | Internal combustion engine with coaxial camshaft and balance shaft |
| US20220403876A1 (en) * | 2019-10-29 | 2022-12-22 | ASF Technologies ( Australia ) Pty Ltd | Internal combustion engine having targeted engine lubrication |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE69101915T2 (en) * | 1990-02-21 | 1994-11-24 | Collins Motor Corp. Ltd., Perth, Westaustralien | LINKED ROTATING AND WALKING MOTION. |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE409919C (en) * | 1923-06-26 | 1925-02-16 | Gottfried Hillekum | Two-stroke internal combustion engine with two opposing cylinders |
| DE3218339A1 (en) * | 1982-05-14 | 1983-11-24 | Ficht GmbH, 8011 Kirchseeon | CRANKSHAFT ARRANGEMENT FOR AN INTERNAL COMBUSTION ENGINE WITH AT LEAST TWO CYLINDERS OVERLAYING FROM OTHER |
| DE3218311A1 (en) * | 1982-05-14 | 1983-11-24 | Ficht GmbH, 8011 Kirchseeon | CRANKSHAFT ARRANGEMENT FOR INTERNAL COMBUSTION ENGINES, ESPECIALLY TWO-STROKE INTERNAL COMBUSTION ENGINES WITH CYLINDERS OVERLAY FROM OTHER |
| DE3447663A1 (en) * | 1984-12-28 | 1986-07-10 | Ficht GmbH, 8011 Kirchseeon | MULTI-CYLINDER COMBUSTION PISTON |
-
1987
- 1987-10-09 GB GB878723712A patent/GB8723712D0/en active Pending
-
1988
- 1988-10-10 WO PCT/GB1988/000839 patent/WO1989003477A1/en unknown
- 1988-10-10 KR KR1019890701042A patent/KR890701876A/en not_active Application Discontinuation
- 1988-10-10 AU AU25457/88A patent/AU2545788A/en not_active Abandoned
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE409919C (en) * | 1923-06-26 | 1925-02-16 | Gottfried Hillekum | Two-stroke internal combustion engine with two opposing cylinders |
| DE3218339A1 (en) * | 1982-05-14 | 1983-11-24 | Ficht GmbH, 8011 Kirchseeon | CRANKSHAFT ARRANGEMENT FOR AN INTERNAL COMBUSTION ENGINE WITH AT LEAST TWO CYLINDERS OVERLAYING FROM OTHER |
| DE3218311A1 (en) * | 1982-05-14 | 1983-11-24 | Ficht GmbH, 8011 Kirchseeon | CRANKSHAFT ARRANGEMENT FOR INTERNAL COMBUSTION ENGINES, ESPECIALLY TWO-STROKE INTERNAL COMBUSTION ENGINES WITH CYLINDERS OVERLAY FROM OTHER |
| DE3447663A1 (en) * | 1984-12-28 | 1986-07-10 | Ficht GmbH, 8011 Kirchseeon | MULTI-CYLINDER COMBUSTION PISTON |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1990014501A1 (en) * | 1989-05-22 | 1990-11-29 | Collins Motor Corporation Limited | Multi-cylinder positive displacement machines |
| CN112746896A (en) * | 2019-10-29 | 2021-05-04 | 赛德动力科技(广东)有限公司 | Internal combustion engine with improved oil pump device |
| CN112746897A (en) * | 2019-10-29 | 2021-05-04 | 赛德动力科技(广东)有限公司 | Internal combustion engine with targeted engine lubrication |
| CN112746900A (en) * | 2019-10-29 | 2021-05-04 | 赛德动力科技(广东)有限公司 | Internal combustion engine with coaxial camshaft and balance shaft |
| US20220403876A1 (en) * | 2019-10-29 | 2022-12-22 | ASF Technologies ( Australia ) Pty Ltd | Internal combustion engine having targeted engine lubrication |
| CN112746897B (en) * | 2019-10-29 | 2024-10-01 | 赛德动力科技(广东)有限公司 | Internal combustion engine with targeted engine lubrication |
| CN112746896B (en) * | 2019-10-29 | 2024-11-05 | 赛德动力科技(广东)有限公司 | Internal combustion engine with improved engine oil pump device |
| CN112746900B (en) * | 2019-10-29 | 2024-11-05 | 赛德动力科技(广东)有限公司 | Internal combustion engine with coaxial camshaft and balance shaft |
Also Published As
| Publication number | Publication date |
|---|---|
| KR890701876A (en) | 1989-12-22 |
| GB8723712D0 (en) | 1987-11-11 |
| AU2545788A (en) | 1989-05-02 |
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